Bearing assembly adjustable spacer and system for adjusting the same

ABSTRACT

A system for adjusting an adjustable spacer is provided. A high-compression section is adapted to receive the spacer for a bearing assembly. A low-compression section is adapted to receive the bearing assembly. In one aspect, a transfer frame can serve as a mechanical interface between the high-compression section and the low-compression section. Also, the transfer frame can be adapted to transfer to the low-compression section a first travel indicative of a first compression of the spacer with the high-compression section. A sensor can be coupled with the high-compression section and the low-compression section. Further, the sensor can serve to limit the first compression according to a second travel indicative of a second compression of the bearing assembly with the low-compression section. Additionally, the first travel and the second travel are preferably related to provide a desired adjustment (e.g., preloading) to the spacer.

TECHNICAL FIELD

This invention relates, generally, to the field of spindle mountedbearings and, more particularly, to an adjustable spacer placed betweensuch bearings mounted on a spindle or the like, as well as a system foradjusting such an adjustable spacer.

BACKGROUND ART

Anti-friction bearings serve to decrease friction of and provide supportfor, for example, a hub upon which a wheel is mounted, for instance, torotate about a spindle. Such bearings may comprise roller bearings, forexample, tapered roller bearings. The spindle may comprise, forinstance, an axle or a shaft.

A typical tapered roller bearing includes a cone having an inner racefor mounting on a spindle, a cup having an outer race for mounting in ahub, and a plurality of roller elements within a roller cage positionedbetween the inner and outer races. Commonly, a pair of such taperedroller bearings are mounted on a spindle for rotation thereabout of awheel mounted on a hub. Cooperating bearings, such as a pair of taperedroller bearings, may be included in a bearing assembly.

In order to properly secure bearings in many axle, spindle, andtransmission assemblies, it is necessary to retain the bearings tightlyunder a predetermined axial load on the shaft or axle, so that they willmaintain the proper running clearance of the roller elements under theinfluence of the combined axial and radial forces which they aredesigned to support. It is often the practice of manufacturers of suchassemblies to carefully measure the space between the bearing innerraces, and provide a spacer of precisely the correct dimension and loadrequirements to fit therebetween. The spacer is often made of groundsteel tubing to a length tolerance of plus or minus one half of onethousandth of an inch. If the bearings are not maintained at a properload the bearings may not roll properly or may prematurely wear,particularly if the bearings are maintained at too high of a load, ormay, if maintained under too low of a load, have excessive play causingfailure of the bearings and wheel supported thereon.

Certain assemblies employ an adjustable spacer or load ring which can befitted by means of loading within the assembly. In assemblies which aresubject to high loading during service, it may be required that thespacer have a very high capacity to resist being deformed. In oneexample, an adapter sleeve optionally may be employed in conjunctionwith the spacer between a pair of roller bearings, such as foraccommodation of differing spindle dimensions at each bearing location.

An exemplary embodiment of such an adapter sleeve and adjustable spaceris disclosed in commonly owned U.S. Pat. No. 5,549,397 to Rode (entitled“Adapter Sleeve and an Adjustable Spacer With Radial Extension UseableThereon” and issued Aug. 27, 1996) and in commonly owned U.S.application Ser. No. 08/661,349 of Rode (entitled “Adjustable BearingAssembly and Adapter Sleeve Therefor” and filed Jun. 14, 1996), whichare hereby incorporated herein by reference in their entireties.

One approach to preparing a bearing assembly with an adjustable spacerwhich is subject to high-shock loading, requires sensing of theresistance to rolling torque that is encountered when a tapered rollerbearing is loaded axially. The sensed resistance is used as an indicatorof whether the bearings are correctly positioned.

However, some assemblies do not permit such an approach, such as wherethe bearing is pre-assembled as a cone and cup assembly with alubrication seal. In particular, the seal, when new, can cause asignificant resistance to rolling torque, thereby interfering with theability to sense the rolling drag of a lightly-preloaded bearing.

In other designs, it may be preferable to use a method of adjusting thespacer without relying upon torque resistance measurement.Unfortunately, such a method can undesirably require the making ofdimensional measurements, which are desirable to avoid since they aretime-consuming and allow errors to be introduced by the assembler.

Thus, a need exists for improving performance, easing use, andincreasing adjustability of an adjustable spacer employed with a bearingassembly. A further need exists for improving ease, accuracy, andcontrol of adjustment to an adjustable spacer employed with a bearingassembly. A need also exists for decreasing dimensional measurementsrequired to properly prepare a spacer and bearing assembly. Anadditional need exists for decreasing the number of parts, and attendantpositioning complexity, required to satisfy a function provided by anadapter sleeve and an adjustable spacer employed with a bearingassembly.

SUMMARY OF THE INVENTION

Pursuant to the present invention, shortcomings of the existing art areovercome and additional advantages are provided through the provision ofa bearing assembly adjustable spacer and a system for adjusting thesame. In one aspect of the invention, a spacer-adjustment systemincludes a high-compression section and a low-compression section. Thehigh-compression section is adapted to receive a spacer for a bearingassembly. The low-compression section is adapted to receive the bearingassembly. Also, a selected limit of travel during compression of thebearing assembly with the low-compression section, serves to provide adesired adjustment to the spacer with the high-compression section.

In another aspect of the invention, the desired adjustment can comprisea preload. The bearing assembly can include a bearing housing, a hub, afirst bearing, a second bearing and/or a displacement gage. Also, thedisplacement gage can be adapted to separate the first and secondbearings by a gaged distance. The low-compression section can serve tosubstantially replicate a selected spindle for mounting of the bearingassembly.

The high-compression section can include a hydraulic cylinder, anelectrohydraulic mechanism, and/or a lead screw device for providing thedesired adjustment to the spacer. A sensor can signal the hydrauliccylinder and/or the electrohydraulic mechanism to halt compression foraccomplishment of the desired adjustment. A sensor can activate a brakefor the lead screw device to accomplish the desired adjustment.

The selected limit of travel can be signalled by a sensor. The sensorcan comprise a pressure switch. The sensor can be adapted to be adjustedto account for a deflection of the sensor upon a contact thereof.

The high-compression section can be connected with the low-compressionsection for transfer therebetween of a dimension of space remaining inthe bearing assembly for the spacer. The dimension of space can beemployed in providing the desired adjustment to the spacer.

A transfer frame, an air cylinder, and/or a tie bar can serve to connectthe high-compression section with the low-compression section. Thehigh-compression section can be adapted to exert a high force on thespacer. Also, the low-compression section can be adapted to exert a lowforce on the bearing assembly. Further, the high force and the low forcecan have a scaled relationship.

The low-compression section can include a mechanism for assuring thedesired adjustment allows proper seating of at least one component ofthe bearing assembly. The mechanism can comprise a device for rotatingat least the at least one component of the bearing assembly.

In yet another aspect of the present invention, a spacer-adjustmentsystem includes a high-compression section and a low-compressionsection. The high-compression section is adapted to receive a spacer fora bearing assembly. The low-compression section is adapted to receivethe bearing assembly. A transfer frame serves as a mechanical interfacebetween the high-compression section and the low-compression section.Also, the transfer frame is adapted to transfer to the low-compressionsection a first travel indicative of a first compression of the spacerwith the high-compression section. A sensor is coupled with thehigh-compression section and the low-compression section. Further, thesensor serves to limit the first compression according to a secondtravel indicative of a second compression of the bearing assembly withthe low-compression section. Additionally, the first travel and thesecond travel are related to provide a desired adjustment to the spacer.

The invention further contemplates a method for deforming a spaceruseable for separating bearings mounted on a spindle. The spacer isplaced in a variable length adjustment chamber of a high-compressionsection. The bearings are positioned in a low-compression section. Also,the positioning of the bearings serves to resemble an arrangement of thebearings separated by the spacer on the spindle. The length adjustmentchamber is decreased to exert a first compressive force on the spacer. Asecond compressive force is applied on the bearings according to aselected relationship between the spacer and at least one of thebearings and/or the spindle. There is sensed a result in thelow-compression section of the second compressive force. The result isemployed to limit the decreasing of the variable length adjustmentchamber, and provide the spacer with a desired adjustment.

In a further aspect of the invention, the selected relationship betweenthe spacer and at least one of the bearings and/or the spindle can beconfigured for transfer between the high-compression section and thelow-compression section of a dimension of space between the bearings,for the spacer. At least one component of the bearings can be rotated toassure proper seating thereof.

Thus, the present invention advantageously provides improvedperformance, easier use, and increased adjustability of an adjustablespacer employed with a bearing assembly. Further, the invention improvesease, accuracy, and control of adjustment to an adjustable spaceremployed with a bearing assembly. Also, the present invention decreasesrequirements for dimensional measurements to properly prepare a spacerand bearing assembly. Additionally, the invention decreases the numberof parts, and attendant positioning complexity, required to satisfy afunction provided by an adapter sleeve and an adjustable spacer employedwith a bearing assembly.

BRIEF DESCRIPTION OF THE DRAWINGS

The subject matter which is regarded as the invention is particularlypointed out and distinctly claimed in the claims at the conclusion ofthe specification. The foregoing and other objects, features, andadvantages of the invention will be readily understood from thefollowing detailed description of preferred embodiments taken inconjunction with the accompanying drawings in which:

FIG. 1 is a cutaway, sectional, partial, side view of one example of anadjustable spacer in a bearing assembly between a spindle and a hubincorporating and using the capabilities of the present invention;.

FIG. 2 is a cutaway, sectional, partial, elevation, side view of oneexample of a system for adjusting the adjustable spacer of FIG. 1incorporating and using the capabilities of the present invention;

FIG. 3 is a cutaway, sectional, partial, elevation, side representationof another example of a system for adjusting the adjustable spacer ofFIG. 1 incorporating and using the capabilities of the presentinvention;

FIG. 4 is a sectional, side view of a first exemplary embodiment of theadjustable spacer of FIG. 1, in accordance with the principles of thepresent invention;

FIG. 5A is a sectional, side view of a second exemplary embodiment ofthe adjustable spacer of FIG. 1, in accordance with the principles ofthe present invention;

FIG. 5B is an isometric view of the adjustable spacer of FIG. 5A, inaccordance with the principles of the present invention.

FIG. 6 is a sectional, side view of a third exemplary embodiment of theadjustable spacer of FIG. 1, in accordance with the principles of thepresent invention; and

FIG. 7 is a sectional, side view of a fourth exemplary embodiment of theadjustable spacer of FIG. 1, in accordance with the principles of thepresent invention.

BEST MODE FOR CARRYING OUT THE INVENTION

In accordance with the principles of the present invention, a system foradjusting an adjustable spacer is provided.

Examples of an adjustable spacer and a system for adjusting the same,incorporating and using the novel features of the present invention aredepicted in the Figures and described in detail herein.

In an exemplary embodiment depicted in FIG. 1, bearing assembly 100includes inner and outer bearings 102 and 104, respectively. Forpurposes of illustration, FIG. 1 depicts the bearings mounted on aspindle which comprises axle 106. Such a spindle may comprise a shaft.The bearings may include, for instance, a pair of identical but opposedtapered roller bearings, as depicted in FIG. 1. In addition, one or moreof the bearings may comprise an unsealed or a sealed bearing, as will beunderstood by those skilled in the art. Further below is discussed amechanism which may be employed to accommodate use of a sealed bearing.

Bearings 102 and 104 support, for example, a bearing housing or hub 108(FIG. 1). As will be understood by those skilled in the art, the hub maysupport any appropriate component(s) of, for instance, a wheel or tire(not shown). Furthermore, adjustable spacer 110 (FIG. 1) may be locatedaxially between the bearings and radially between axle 106 and the hub,as described herein.

Referring to FIG. 1, bearing 102 may comprise a tapered roller bearingwhich includes inner race 112 mounted on axle 106, outer race 114mounted in hub 108, and roller elements 116 positioned between the innerand outer races. Similarly, bearing 104 may comprise a tapered rollerbearing which includes inner race 122 mounted on the axle, outer race124 mounted in the hub, and roller elements 126 positioned between theinner and outer races 122 and 124, respectively. One or more of thebearing may employ roller cage(s) 125 in order to hold roller elements116, 126 in proper position between the corresponding inner and outerraces, as will be understood by those skilled in the art.

Still referring to FIG. 1, axle 106 may include shoulder 128 forreceiving inner race 112 of inner bearing 102. Furthermore, the axle mayinclude screw thread(s) 130 for receiving nut 132. The nut may thus betightened, such as to abut inner race 122 of outer bearing 104, forcooperative provision of axial support among bearing assembly 100,adjustable spacer 110, hub 108 and the axle, as described herein.

In one example, as depicted in FIG. 1, hub 108 may be mounted on outerraces 114 and 124 for rotation about axle 106, with roller elements 116positioned between the outer race 114 and inner race 112, and rollerelements 126 positioned between the outer race 124 and inner race 122,where the inner races may be mounted on the axle. In an alternativeembodiment, the axle may rotate within the hub, in accordance with theprinciples of the present invention. That is, the axle and/or the hubcould serve as, and/or resemble, a stator and/or a rotor, as will beappreciated by those skilled in the art. For purposes of illustration,the description herein emphasizes an embodiment in which the axle servesas a stator, and the hub serves as a rotor.

As illustrated in FIG. 1 for explanatory purposes, hub 108 may includeinner shoulder 134 and outer shoulder 136. The inner shoulder may serveto receive outer race 114 of inner bearing 102. The outer shoulder mayserve to receive outer race 124 of outer bearing 104.

In accordance with the principles of the present invention, adjustablespacer 110 may include inner end 138 and outer end 139. In one example,the inner end may axially abut inner race 112 of inner bearing 102, andmay radially abut a first location on axle 106. Also, the outer end mayaxially abut inner race 122 of outer bearing 104, and may radially abuta second location on the axle. In an alternative embodiment, where theaxle may serve as a rotor and hub 108 may serve as a stator, theadjustable spacer preferably would axially abut outer races 114 and 124and radially abut location(s) of the hub, rather than location(s) on theaxle, as will be appreciated by those skilled in the art.

Referring to FIG. 1, adjustable spacer 110 preferably includes bend 140.In one example, the bend may serve to allow adjustment to, for instance,axial length of the adjustable spacer, and/or other characteristic(s)and/or behavior(s) of the adjustable spacer. As described herein,adjustment(s) to the bend may allow, for example, preloading of bearingassembly 100. Preloading of the adjustable spacer may be necessary toallow for the proper axial loading on the bearing assembly, includingthe adjustable spacer. Proper axial loading may be necessary to allowthe bearings to obtain optimal performance and maximal life, withsubstantial elimination of play therein.

Moreover, referring still to FIG. 1, adjustable spacer 110 may includeflange 142. The flange may serve to allow, for instance, positioning ofinner bearing 102 about a first diameter of axle 106 which is differentfrom a second diameter of the axle about which outer bearing 104 ismounted, as depicted in FIG. 1 for purposes of illustration. Suchflange(s) may be formed at any appropriate location(s) of the adjustablespacer, and/or with respect to any appropriate location(s) of, forinstance, the axle, as will be appreciated by those skilled in the art.

Additional description of exemplary feature(s) for adjustable spacer 110appears further below.

FIG. 2 depicts an exemplary system 200 for providing adjustment(s) toadjustable spacer 110. In accordance with the principles of the presentinvention, the system may serve to advantageously provide the adjustablespacer with, for instance, a desired preload suited to the actualtolerance(s) of, for example, bearings 102 and 104 and hub 108 beforemounting and axial loading thereof, such as about axle 106 (FIG. 1), asdescribed herein.

In one example, system 200 includes outer frame 202 which includesproximal and distal platforms 203 and 204, respectively. The outer framemay house high-compression section 206 and low-compression section 208.The high-compression section includes base 210, which includes proximaland distal walls 212 and 214, respectively, and linear-transfer frame216, which includes proximal and distal walls 218 and 220, respectively.

In accordance with the principles of the present invention, bearings 102and 104 and hub 108 are positioned in low-compression section 208 foradjustment and crushing (e.g., preloading of) adjustable spacer 110,which is positioned separately in high-compression section 206, asdescribed herein. Preferably, the bearings, the hub, and the adjustablespacer are subsequently assembled together, as depicted in FIG. 1.

Referring to FIG. 2, base 210 may be supported with proximal platform203. Further, the base and linear-transfer frame 216 may have atelescopic engagement, which may be employed to define variable lengthadjustment chamber 222, which is preferably suited for receiving andadjusting adjustable spacer 110, as described herein.

Further, base 210 may house a prime mover such as hydraulic cylinder 224with piston 226, or, in an alternative embodiment, an electrohydraulicmechanism and/or a mechanical lead screw device, as will be understoodby those skilled in the art. In one example, actuation of the hydrauliccylinder in order to extend the piston distally, serves to advanceproximal wall 218 of linear-transfer frame 216 toward distal wall 214 ofthe base, and (e.g., linearly) decrease length adjustment chamber 222 asit holds adjustable spacer 110, in accordance with the principles of thepresent invention. Furthermore, proximal retraction of the pistonresults in proximal wall 218 retreating proximally from distal wall 214,for (e.g., linear) increase of the length adjustment chamber holding theadjustable spacer.

Base 210, in one example, may be formed to withstand high forces withvery small deflections. Preferably, the base is constructed to deflectless than 0.001 in. under a force of fifty thousand pounds.

For illustrative purposes, FIG. 2 may be considered to depict system 200with an axial orientation generally opposed to an effective direction ofgravitational force. While part(s) of the description herein, forexplanatory purposes, may imply certain exemplary direction(s), suchdirection(s) may be considered relative. As will be appreciated by thoseskilled in the art, the significance of, for example, a “verticallyupward” direction in many environments stems from its opposition to adominant “downwardly” acting gravitational force, resulting from thepresence of a large mass such as the Earth, where “vertical”approximates radial alignment therewith. Furthermore, a “horizontal”direction and a “vertically upward” direction can be readily ascertainedfollowing determination of an appropriate “downward” direction.

Design choice(s) allow accommodation(s) of any orientation(s) for anysystem(s) in accordance with the principles of the present invention.

Referring to FIG. 2, sufficient distal advancement of proximal wall 218of linear-transfer frame 216 toward distal wall 214 of base 210 servesto engage adjustable spacer 110 with both walls 214 and 218. Thereafter,additional distal advancement results in application to the adjustablespacer of a (e.g., linear) compressive force. In accordance with theprinciples of the present invention, the compressive force can serve toaxially deform or crush the adjustable spacer, such as for preloadingthereof. Moreover, bend 140 may be formed with a relatively-decreasedradial thickness, as depicted in FIG. 1, which may serve to concentratethereat compressive force(s) applied axially to the adjustable spacer,as will be appreciated by those skilled in the art.

In one aspect, high-compression section 206 may serve to desirablypreload adjustable spacer 110 according to actual tolerance(s) and/orother physical characteristic(s) of bearings 102 and 104 as well as hub108, as described herein.

Referring to FIG. 2, high-compression section 206 may supportlow-compression section 208. In one example, distal wall 220 oflinear-transfer frame 216 may serve as a mechanical interface betweenthe high-compression and low-compression sections, as described herein.

As depicted in FIG. 2 for illustrative purposes, low-compression section208 includes spring-loaded mount 250, which may be mounted to distalwall 220 of linear-transfer frame 216. So, (e.g., linear) movement ofthe linear-transfer frame may be transferred from high-compressionsection 206 to the low-compression through distal wall 220. Also,hydraulic cylinder 224, by actuation, through piston 226, of distaladvancement and proximal retraction of distal wall 218 of thelinear-transfer frame, can distally advance and proximally retract thespring-loaded mount of the low-compression section.

Referring to FIG. 2, spring-loaded mount 250, in one embodiment,supports inner bearing 102. Namely, the spring-loaded mount receivesinner race 112 of the inner bearing. Additionally, the inner race 112 inturn supports spring-loaded cone gage 252, which serves as a proxy foraxle 106 (FIG. 1), as described herein. Furthermore, the inner bearingpartially supports hub 108. That is, outer race 114 receives innershoulder 134. Additionally, the spring-loaded cone gage supports innerrace 122 of outer bearing 104, as described herein.

For explanatory purposes, FIG. 2 depicts a mechanism which allows, forinstance, outer bearing 104 to comprise, for example, a sealed bearing.As will be appreciated by those skilled in the art, use of a sealedbearing for one or more of bearings 102 and 104 presents a challenge,owing to the undesirability of damaging the sealed bearing(s), such asduring removal from low-compression section 208, for example, in orderto be subsequently installed on axle 106, as depicted in FIG. 1. In oneaspect, the present invention addresses this challenge withcone-displacement gage 254, as described herein.

As depicted in FIG. 2, cone-displacement gage 254 includes inner end 256and outer end 258, which serve to substantially replicate a mechanicalinterface, that is depicted in FIG. 1, between outer race 124 andshoulder 136. Namely, as depicted in FIG. 2, by seating the inner end256 at the shoulder 136, and seating outer race 124 at the outer end258, the cone-displacement gage serves to simply add an axial offsetrepresented by gage length C3. Accommodation of the axial offsetrepresented by gage length C3 in performing adjustment of adjustablespacer 110 is discussed further below. Moreover, an additional mechanismsimilar to the cone-displacement gage could also be employed, forexample, should bearing 102 comprise a sealed bearing, as will beappreciated by those skilled in the art.

FIG. 3 represents another exemplary system, namely, system 200′, servingto illustrate a system such as system 200 (FIG. 2) at a time whencone-displacement gage 254 (FIG. 2) is not used, as will be appreciatedby those skilled in the art. In contrast to system 200, system 200′abuts outer race 124 with shoulder 136. For example, system 200′ mayadvantageously be employed when neither roller bearing 102 nor rollerbearing 104 is a sealed bearing, in accordance with the principles ofthe present invention. In one example, cone gage 252′, which serves as aproxy for axle 106 (FIG. 1), may be supported by inner race 112, and maysupport inner race 122 of outer bearing 104, as described herein.

Returning to FIG. 2, spring-loaded clamp 260 may be mounted to distalplatform 204 for abutment with inner race 122. Additionally, the distalplatform may serve to adjustably support, for example, a sensor such astravel sensor 262 (e.g., a pressure switch). In one example, the travelsensor is capable of sensing contact with cone gage 252 at a low,predetermined level of contact force, as described herein. Also, thedistal platform may be moved axially with, for instance, air liftcylinder(s) 264. In an alternative embodiment, tie bar(s) may be used,as will be understood by those skilled in the art.

With reference to the Figures, exemplary operation of systems inaccordance with the present invention is now described, starting withinitialization and calibration thereof. Referring to FIG. 2, hydrauliccylinder 224 may retract piston 226 proximally. Air cylinder(s) 264 maybe extended axially, in order to distally extend distal platform 204.

Calibration may be performed as follows. As will be appreciated by thoseskilled in the art, two solid gage blocks (not shown), one solid gageblock for high-compression section 206 and another solid gage block forlow-compression section 208, may be employed for calibration, asdescribed below.

Referring again to FIG. 2, the first solid gage block may be placed inhigh-compression section 206 at length adjustment chamber 222, asindicated by first gage length P1. The second solid gage block may beplaced in low-compression section 208 as indicated by second gage lengthP2. In particular, the second gage length is preferable selected tosubstantially equal the sum of the length of the first gage length plusa number of gage length(s), of the low-compression section, as will beappreciated by those skilled in the art.

In one example, as depicted in FIG. 2, second gage length P2 equalsfirst gage length P1 plus gage lengths C1, C2, and C3. In anotherexample, as depicted in FIG. 3, the second gage length P2 equals thefirst gage length P1 plus gage lengths C1 and C2. In particular, system200′ (FIG. 2) lacks gage length C3 (FIG. 2), owing to the omission ofcone-displacement gage 254 (FIG. 2), as discussed above.

Further referring to FIG. 2, air cylinder(s) 264 may be retractedaxially, in order to proximally retract distal platform 204 and clampthe second solid gage block, indicated by second gage length P2, inlow-compression section 208. Next, the first solid gage block, indicatedby first gage length P1, is clamped in high-compression section 206.Now, travel sensor 262 is set to a desired reading contacting the secondsolid gage block in the low-compression section, in accordance with theprinciples of the present invention. At this point, system 200 iscalibrated, as will be appreciated by those skilled in the art.

Pressure in hydraulic cylinder 226 and air cylinder(s) 264 may berelaxed, and distal platform 204 may be extended distally. The first andsecond solid gage blocks may be removed, and preferably stored awaysafely. As will be appreciated by those skilled in the art, the abovecalibration should only have to be performed once, but can be checked bya user (e.g., a customer of the system) easily, and as often as requiredand/or desired, in accordance with the principles of the presentinvention.

As depicted in FIG. 3, a system of the present invention, such as system200′ or system 200 (FIG. 2), may be advantageously arranged so axialdistance A1, between travel sensor 262 and spring-loaded cone gage 252′(or spring-loaded cone gage 252, as depicted in FIG. 2), issubstantially equal to axial distance A2, between distal end ofadjustable spacer 110 and distal wall 214, plus a selected preload forthe adjustable spacer, in accordance with the principles of the presentinvention.

With reference to the Figures, now are described exemplary steps forproduction use of system(s) of the present invention. In one example,adjustable spacer 110 is positioned in variable length adjustmentchamber 222 of high-compression section 206, as depicted in FIG. 2. Hub108 with inner bearing 102 is set on spring-loaded mount 250.Spring-loaded cone gage 252 with cone-displacement gage 254 attached aremoved proximally through the hub and the inner bearing. At this point,the proximal end of the spring-loaded cone gage preferably will not yetabut distal wall 220 of linear-transfer frame 216, as will beappreciated by those skilled in the art.

Still referring to FIG. 2, outer bearing 104 is telescoped proximally toabut spring-loaded cone gage 252 and cone-displacement gage 254. In analternative embodiment, as depicted in FIG. 3, the outer bearing wouldbe telescoped proximally to abut the spring-loaded cone gage and hub108.

Referring again to FIG. 2, air cylinder(s) 264 are axially retracted inorder to move distally and position spring-loaded clamp 260, travelsensor 262, and distal platform 204. At this point, in one example, thespring force in the spring-loaded clamp in conjunction with the staticweight of hub 108, serve to overcome the spring force in spring-loadedcone gage 252 and spring-loaded mount 250, until the proximal end of thespring-loaded cone gage abuts distal wall 220 of linear-transfer frame216, at gage length C2. Further, the spring force in the spring-loadedmount preferably serves to keep inner race 112 of inner bearing 102 inabutment with the spring-loaded cone gage. Referring to FIG. 2, the hubwith the inner race of the inner bearing, and cone-displacement gage 254with inner race 124 of outer bearing 104 preferably can be rotated atthis point, because of clearance between the spring-loaded gage and thecone displacement gage. Such rotation may desirably serve to assure thatroller elements 116, 126 (FIG. 1) are properly seated within thebearings. With respect to system 200′ depicted in FIG. 3, the hub withthe inner race of the inner bearing, and the inner race of the outerbearing, obviously could be rotated at such a point.

Again referring to FIG. 2, in one embodiment, the calculation of thespring loads serves to ensure spring-loaded clamp 260 does not overridethe combined loads on spring-loaded mount 250 after the proximal end ofthe spring-loaded cone gage abuts distal wall 220 of linear-transferframe 216, at gage length C2, as will be appreciated by those skilled inthe art. Furthermore, a positive locking clamp comprising thespring-loaded mount, could be employed to clamp from spring-loaded conegage 252 to inner race 112 of inner bearing 102, for ensured abutmenttherebetween.

In one example, hydraulic cylinder 224 now may actuate piston 226 inorder to compress adjustable spacer 110 in length until the distal endof spring-loaded cone gage 252 contacts travel sensor 262, at gagelength C1, in accordance with the principles of the present invention.Preferably, adjustment may be made to account for small deflection(s) ofthe travel sensor upon contact (e.g., at a low predetermined force), andto account for a proper transfer of a dimension of space remaining inbearing assembly 100 for the adjustable spacer, to length adjustmentchamber 222. At contact of the travel sensor, in one embodiment, thehydraulic pressure of the hydraulic cylinder is preferably released, forproximal retraction of piston 224. For instance, such mechanism(s) maybe achieved by employing a hydraulic circuit and/or an electrohydraulicunit (not shown), as will be appreciated by those skilled in the art. Inan alternative embodiment, the travel sensor may signal activation of abrake for a lead screw device, as will be appreciated by those skilledin the art. Furthermore, air cylinder(s) 264 may be axially extended todistally move distal platform 204. Additionally, bearings 102 and 104,the gages 252 and 254 (or simply gage 252′, as depicted in FIG. 3 anddescribed herein), hub 108 and adjustable spacer 110 may be removed, theadjustable spacer having been adjusted and preloaded by crushing withinlength adjustment chamber 222 in accordance with principles of thepresent invention. The adjustable spacer 110, bearings 102 and 104, andhub 108 may then be mounted on an axle or spindle, such as that shown inFIG. 1. When mounted on the axle or spindle 106, the nut 132 istightened to a desired torque setting and the adjustable spacer 110 hasbeen crushed to a length so that the optimal amount of force istranslated therethrough at the desired torque setting. This enables thebearings to rotate at their optimal performance and for maximal life.

For instance, adjustable spacer 110 may be formed with carbon steel tohave an approximate axial length of four inches. In one example, theadjustable spacer may initially have a generally cylindrical shape,and/or a number of generally cylindrical section(s), where machiningthereof may be employed to form desired feature(s), as will beunderstood by those skilled in the art. Typically, when the adjustablespacer is mounted in a bearing assembly as is shown in FIG. 1, thetorque on the nut holding the assembly in place may be about 300 ft-lbs,which creates an axial load through the adjustable spacer and bearingassembly of about 10,000 lbs. For safety reasons, it is preferred tomake the adjustable spacer crushable in length at a force of at leastthree to four times the mounted axial load. Therefore, a 10,000 lbloaded adjustable spacer, preferably should be crushable at a force ofno less than about 40,000 lbs. Accordingly, hydraulic cylinder 224 mustbe capable of applying a force to the length adjustment chambernecessary to crush the adjustable spacer.

For purposes of illustration, a number of preferred implementations ofadjustable spacer 110 of the present invention are described below withreference to the Figures.

As a first exemplary embodiment, FIG. 4 depicts adjustable spacer 410having inner end 438 and outer end 439. In one example, the inner endmay axially abut inner race 112 (FIG. 1) of inner bearing 102 (FIG. 1),and may radially abut a first location on axle 106 (FIG. 1). Also, theouter end may axially abut inner race 122 (FIG. 1) of outer bearing 104(FIG. 1), and may radially abut a second location on the axle.

Adjustable spacer 410 preferably includes bend 440. In one example, thebend may serve to allow adjustment to, for instance, axial length of theadjustable spacer, and/or other characteristic(s) and/or behavior(s) ofthe adjustable spacer. As described herein, adjustment(s) to the bendmay allow, for example, preloading of bearing assembly 100 (FIG. 1),such as for substantial elimination of play therein.

Moreover, adjustable spacer 410 may include flange 442. The flange mayserve to allow, for instance, positioning of inner bearing 102 (FIG. 1)about a first diameter of axle 106 (FIG. 1) which is different from asecond diameter of the axle about which outer bearing 104 (FIG. 1) ismounted. Such flange(s) may be formed at any appropriate location(s) ofthe adjustable spacer, and/or with respect to any appropriatelocation(s) of, for instance, the axle, as will be appreciated by thoseskilled in the art. Preferably, the flange is formed integrally withother component(s) of the adjustable spacer.

As a second exemplary embodiment, FIGS. 5A-5B depict adjustable spacer510 having inner end 538 and outer end 539. In one example, the innerend may axially abut inner race 112 (FIG. 1) of inner bearing 102 (FIG.1), and may radially abut a first location on axle 106 (FIG. 1). Also,the outer end may axially abut inner race 122 (FIG. 1) of outer bearing104 (FIG. 1), and may radially abut a second location on the axle.

Adjustable spacer 510 preferably includes bend 540. In one example, thebend may serve to allow adjustment to, for instance, axial length of theadjustable spacer, and/or other characteristic(s) and/or behavior(s) ofthe adjustable spacer. As described herein, adjustment(s) to the bendmay allow, for example, preloading of bearing assembly 100 (FIG. 1),such as for substantial elimination of play therein.

Moreover, adjustable spacer 510 may include flange 542. The flange mayserve to allow, for instance, positioning of inner bearing 102 (FIG. 1)about a first diameter of axle 106 (FIG. 1) which is different from asecond diameter of the axle about which outer bearing 104 (FIG. 1) ismounted. Such flange(s) may be formed at any appropriate location(s) ofthe adjustable spacer, and/or with respect to any appropriatelocation(s) of, for instance, the axle, as will be appreciated by thoseskilled in the art. Preferably, the flange is formed integrally withother component(s) of the adjustable spacer.

As a third exemplary embodiment, FIG. 6 depicts adjustable spacer 610having inner end 638 and outer end 639. In one example, the inner endmay axially abut inner race 112 (FIG. 1) of inner bearing 102 (FIG. 1),and may radially abut a first location on axle 106 (FIG. 1). Also, theouter end may axially abut inner race 122 (FIG. 1) of outer bearing 104(FIG. 1), and may radially abut a second location on the axle.

Adjustable spacer 610 preferably includes bend 640. In one example, thebend may serve to allow adjustment to, for instance, axial length of theadjustable spacer, and/or other characteristic(s) and/or behavior(s) ofthe adjustable spacer. As described herein, adjustment(s) to the bendmay allow, for example, preloading of bearing assembly 100 (FIG. 1),such as for substantial elimination of play therein.

Moreover, adjustable spacer 610 may include flange 642. The flange mayserve to allow, for instance, positioning of inner bearing 102 (FIG. 1)about a first diameter of axle 106 (FIG. 1) which is different from asecond diameter of the axle about which outer bearing 104 (FIG. 1) ismounted. Such flange(s) may be formed at any appropriate location(s) ofthe adjustable spacer, and/or with respect to any appropriatelocation(s) of, for instance, the axle, as will be appreciated by thoseskilled in the art. Preferably, the flange is formed integrally withother component(s) of the adjustable spacer.

As a fourth exemplary embodiment, FIG. 7 depicts adjustable spacer 710having inner end 738 and outer end 739. In one example, the inner endmay axially abut inner race 112 (FIG. 1) of inner bearing 102 (FIG. 1),and may radially abut a first location on axle 106 (FIG. 1). Also, theouter end may axially abut inner race 122 (FIG. 1) of outer bearing 104(FIG. 1), and may radially abut a second location on the axle.

Adjustable spacer 710 preferably includes bend 740. In one example, thebend may serve to allow adjustment to, for instance, axial length of theadjustable spacer, and/or other characteristic(s) and/or behavior(s) ofthe adjustable spacer. As described herein, adjustment(s) to the bendmay allow, for example, preloading of bearing assembly 100 (FIG. 1),such as for substantial elimination of play therein.

Although preferred embodiments have been depicted and described indetail herein, it will be apparent to those skilled in the relevant artthat various modifications, additions, substitutions and the like can bemade without departing from the spirit of the invention and these aretherefore considered to be within the scope of the invention as definedin the following claims.

What is claimed is:
 1. A spacer-adjustment system for a bearing assemblyof a type having at least one bearing, comprising: a high-compressionsection and a low-compression section, said high compression section andsaid low compression section supported by a frame, said frame separatefrom an axle, spindle or wheel for receiving said bearing assembly; saidhigh-compression section adapted to receive a spacer for said bearingassembly; said low-compression section adapted to receive said bearingassembly; and wherein a selected limit of travel during compression ofsaid bearing assembly with said low-compression section serves toprovide a desired adjustment to said spacer with said high-compressionsection.
 2. The system of claim 1, wherein said desired adjustmentcomprises a preload.
 3. The system of claim 1, wherein said bearingassembly includes at least one of a bearing housing, a hub, a firstbearing, a second bearing and a displacement gage, wherein saiddisplacement gage is adapted to separate said first and second bearingsby a gaged distance.
 4. The system of claim 1, wherein saidlow-compression section serves to substantially replicate a selectedspindle for mounting of said bearing assembly.
 5. The system of claim 1,wherein said high-compression section includes at least one of ahydraulic cylinder, an electrohydraulic mechanism, and a lead screwdevice for providing said desired adjustment to said spacer.
 6. Thesystem of claim 5, wherein a sensor signals at least one of saidhydraulic cylinder and said electrohydraulic mechanism to haltcompression for accomplishment of said desired adjustment.
 7. The systemof claim 5, wherein a sensor activates a brake for said lead screwdevice to accomplish said desired adjustment.
 8. The system of claim 1,wherein said selected limit of travel is signalled by a sensor.
 9. Thesystem of claim 8, wherein said sensor comprises a pressure switch. 10.The system of claim 8, wherein said sensor is adapted to be adjusted toaccount for a deflection of said sensor upon a contact thereof.
 11. Thesystem of claim 1, wherein said high-compression section is connectedwith said low-compression section for transfer therebetween of adimension of space remaining in said bearing assembly for said spacer.12. The system of claim 11, wherein said dimension of space is employedin providing said desired adjustment to said spacer.
 13. The system ofclaim 1, wherein at least one of a transfer frame, an air cylinder, anda tie bar serves to connect said high-compression section with saidlow-compression section.
 14. The system of claim 1, wherein saidhigh-compression section is adapted to exert a high force on saidspacer, wherein said low-compression section is adapted to exert a lowforce on said bearing assembly, and wherein said high force and said lowforce have a scaled relationship.
 15. The system of claim 1, whereinsaid low-compression section includes a mechanism for assuring saiddesired adjustment allows proper seating of at least one component ofsaid bearing assembly.
 16. The system of claim 15, wherein saidmechanism comprises a device for rotating at least said at least onecomponent of said bearing assembly.
 17. A spacer-adjustment system for abearing assembly of a type having at least one bearing, comprising: ahigh-compression section adapted to receive a spacer for said bearingassembly, said high compression section being supported by a supportingframe wherein said frame is separate from an axle, spindle, or wheel forreceiving said bearing assembly; a low-compression section adapted toreceive said bearing assembly wherein said low compression section issupported by said supporting frame; a transfer frame serving as amechanical interface between said high-compression section and saidlow-compression section, wherein said transfer frame is adapted totransfer to said low-compression section a first travel distanceindicative of a first compression of said spacer with saidhigh-compression section; and a sensor coupled with saidhigh-compression section and said low-compression section, wherein saidsensor serves to limit said first compression according to a secondtravel distance indicative of a second compression of said bearingassembly with said low-compression section, wherein said first traveland said second travel distance are related to provide a desiredadjustment to said spacer.
 18. A spacer-adjustment system for a bearingassembly having two sets of bearings, the system comprising: ahigh-compression section and a low-compression section, said highcompression section and said low compression section supported by aframe, said frame separate from an axle, spindle or wheel for receivingsaid bearing assembly; said high-compression section adapted to receivea spacer for the bearing assembly; said low-compression section adaptedto receive the two sets of bearings of the bearing assembly; and whereina selected limit of travel during compression of said bearing assemblywith said low-compression section serves to provide the desiredadjustment to said spacer with said high-compression section.
 19. Thesystem of claim 18, wherein said low-compression section serves tosubstantially replicate a selected spindle for mounting of said bearingassembly.
 20. The system of claim 18, further comprising: a transferframe serving as a mechanical interface between said high-compressionsection and said low-compression section, wherein said transfer frame isadapted to transfer to said low-compression section a first traveldistance indicative of a first compression of said spacer with saidhigh-compression section; and a sensor coupled with saidhigh-compression section and said low-compression section, wherein saidsensor serves to limit said first compression according to a secondtravel distance indicative of a second compression of said bearingassembly with said low-compression section, wherein said first traveldistance and said second travel distance are related to provide adesired adjustment to said spacer.